Rotary damper and braking system

Abstract

A rotary damper (1) suitable for use as a brake pedal damper with fail-safe function is provided. In the rotary damper (1) for automobile brake pedal that generates damping torque when the housing (11) rotates in the forward direction (N) relative to the rotor (12), the housing (11) is formed of thermoplastic resin, and the housing (11) is provided with a pair of radially outward protruding arms (19a, 19b) that clamp and rotate around the pedal rotation center (O) in conjunction with the brake pedal (4). In addition, the arm (19a) of the pair of arms (19a, 19b) located downstream in the forward direction (N) is provided with a curved portion (191) of constant width, and the plate (5) is supported by a support portion (192) located at a position closer to the end of the curved portion (191).

Description

Technical Field

[0001] This invention relates to rotary dampers, and more particularly to rotary dampers suitable for brake pedal dampers. Background Technology

[0002] Rotational dampers are known to generate strong damping torque for rotation in the forward direction and weak damping torque for rotation in the reverse direction. For example, Patent Document 1 discloses a rotational damper that is simple in structure and can be manufactured inexpensively.

[0003] The rotary damper described in Patent Document 1 comprises: a shell having a cylindrical chamber; a rotor rotatably housed within the cylindrical chamber; a viscous fluid filling the cylindrical chamber; and a cover installed on the open side end face of the shell and sealing the rotor together with the viscous fluid within the cylindrical chamber.

[0004] The rotor has: a cylindrical rotor body; and blades that protrude radially outward from the outer peripheral surface of the rotor body, forming a small gap with respect to the sidewall of the cylindrical chamber. A flow path is formed in the blades, extending from one side (called the first side) to another side (called the second side) along the direction of rotor rotation. Furthermore, a seal is installed on the end face of the blade (the face facing the sidewall of the cylindrical chamber) to fill the small gap between the blade and the sidewall of the cylindrical chamber. This seal has a check valve made of an elastic body that opens and closes the flow path formed in the blades. Additionally, a partition protruding radially inward is formed on the sidewall of the cylindrical chamber, forming a small gap with the outer peripheral surface of the rotor body.

[0005] In the configuration described above, for the rotary damper of Patent Document 1, if a force is applied to the rotor in the direction of rotation from the first side of the blade to the second side (forward rotation), the viscous fluid in the cylindrical chamber pushes the check valve towards the second side of the blade, blocking the flow path. Thus, the movement of the viscous fluid is restricted only through the gap between the partition of the cylindrical chamber and the outer peripheral surface of the rotor body, and the gap between the closed-side end face (bottom surface) of the outer shell and the lower surface of the blade (the surface facing the closed-side end face of the outer shell). The pressure of the viscous fluid on the second side of the blade increases, generating a strong damping torque. On the other hand, if a force is applied to the rotor in the direction of rotation from the second side of the blade to the first side (reverse rotation), the viscous fluid on the first side of the blade flows into the flow path, pushing up the check valve and releasing the flow path. Therefore, since the movement of the viscous fluid also occurs in the flow path formed in the blade, the pressure of the viscous fluid on the first side of the blade does not increase, resulting in a weak damping torque.

[0006] Prior art literature

[0007] Patent documents

[0008] Patent Document 1: Japanese Patent Application Publication No. 7-301272 Summary of the Invention

[0009] The problem that the invention aims to solve

[0010] The rotary damper described in Patent Document 1 generates a strong damping torque when the driver of the car depresses the brake pedal, and can be used as a damper for the car brake pedal.

[0011] However, when the rotary damper described in Patent Document 1 is used as a damper for automobile brake pedals, from the viewpoint of failure protection, even if the rotary damper malfunctions and the relative rotation between the housing and the rotor is obstructed, it is necessary to ensure that braking can be reliably applied by forcefully pressing the brake pedal.

[0012] The present invention was made in view of the above circumstances, and its object is to provide a rotary damper suitable as a brake pedal damper with fail-safe function, and a braking system using the rotary damper.

[0013] Solution for solving the problem

[0014] To address the aforementioned issues, the present invention provides a rotary damper for automotive brake pedals. When the housing rotates relative to the rotor in the forward direction, a damping torque is generated. The housing is formed of thermoplastic resin and has a pair of arms protruding radially outward. These arms hold a plate that rotates around the pedal's rotation center in conjunction with the brake pedal. Furthermore, one of the arms, located downstream in the forward direction, has a curved portion of constant width, and a plate is supported on this arm at a position closer to its end than the curved portion.

[0015] For example, the rotary damper of the present invention is a rotary damper for an automobile brake pedal. This rotary damper includes a rotor and a housing that rotatably houses the rotor. If the housing rotates relative to the rotor in the forward rotation direction, a damping torque is generated.

[0016] The aforementioned housing is formed of thermoplastic resin and has a pair of arms protruding radially outward, which clamp a plate that rotates around the pedal's rotation center in conjunction with the brake pedal.

[0017] The arm located downstream of the aforementioned pair of arms in the forward rotation direction has:

[0018] A curved section with a constant width; and

[0019] A support portion is located at a position closer to the end of the aforementioned curved portion and supports the aforementioned plate.

[0020] Furthermore, the braking system of the present invention includes the aforementioned rotary damper, wherein,

[0021] The above-mentioned braking system includes:

[0022] A shaft is positioned at the center of rotation of the pedal;

[0023] A brake arm, which is rotatably mounted on the aforementioned shaft and connected to the master cylinder;

[0024] A brake pedal, which is mounted at the end of the aforementioned brake arm; and

[0025] A plate, which is mounted on the brake arm in a manner that rotates around the pedal's rotation center in conjunction with the brake pedal.

[0026] The aforementioned rotary damper fixes the rotor to the aforementioned shaft and constrains the rotation of the rotor about the rotation center of the aforementioned pedal.

[0027] The aforementioned rotary damper is installed as follows: when the brake pedal is depressed and the plate rotates about the pedal's rotation center in the forward direction, the plate is supported by the support portion of the arm located downstream in the forward direction of rotation; when the brake pedal is released and the plate rotates about the pedal's rotation center in the reverse direction, the plate is supported by the arm located upstream in the forward direction of rotation.

[0028] The plate is clamped and held by the pair of arms in a manner that does not interfere with the base portion between the pair of arms.

[0029] The effects of the invention

[0030] In this invention, a rotational damper is provided such that a plate presses against the arm located downstream in the forward rotation direction in conjunction with the depressing of the brake pedal, thereby generating a damping torque relative to the depressing of the brake pedal. Furthermore, since the outer shell is formed of thermoplastic resin, and a curved portion is provided in the arm located downstream in the forward rotation direction, with a support plate on the portion of the arm closer to the end of the curved portion, the stress generated in the arm due to the pressing of the plate is concentrated in the curved portion. Therefore, even if the rotational damper malfunctions and the relative rotation between the outer shell and the rotor is hindered, braking can be applied by forcefully depressing the brake pedal, causing the curved portion to break. Moreover, since the width of the curved portion is kept constant, the deviation in the brake pedal depressing force required to break the curved portion due to deviations in the pressing direction of the plate applied to the portion of the arm closer to the end of the curved portion can be reduced.

[0031] Therefore, according to the present invention, a rotary damper suitable as a brake pedal damper with fail-safe function and a braking system using the rotary damper can be provided. Attached Figure Description

[0032] Figure 1 (A) Figure 1 (C) is a front view, a side view, and a rear view of the rotary damper 1 according to an embodiment of the present invention.

[0033] Figure 2 (A) is Figure 1 (A) shows the A-A sectional view of the rotary damper 1. Figure 2 (B) is Figure 1 The B-B cross-sectional view of the rotary damper 1 shown in (B) is shown.

[0034] Figure 3 (A) and Figure 3 (B) is Figure 2 (A) shows an enlarged view of part A and part B of the rotary damper 1.

[0035] Figure 4 (A) is Figure 2 (A) shows an enlarged view of part C of the rotary damper 1. Figure 4 (B) is Figure 2 (B) is an enlarged view of part D of the rotary damper 1.

[0036] Figure 5 (A) is the front view of the outer casing 11. Figure 5 (B) is Figure 5 (A) shows a C-C sectional view of the outer casing 11. Figure 5 (C) is the rear view of the outer casing 11. Figure 5 (D) is Figure 5 (A) shows an enlarged view of part E of the outer casing 11. Figure 5 (E) is Figure 5 (A) shows an enlarged cross-sectional view of the outer casing 11 along line D-D. Figure 5 (F) is Figure 5 (A) shows an enlarged cross-sectional view of the outer shell 11 along the E-E line.

[0037] Figure 6 (A) and Figure 6 (B) is the front view and side view of rotor 12. Figure 6 (C) is Figure 6 The rotor 12 shown in (A) is a cross-sectional view of F-F.

[0038] Figure 7 (A) and Figure 7 (B) is the front view and side view of the first seal 13. Figure 7 (C) is Figure 7(A) is a G-G sectional view of the first seal 13.

[0039] Figure 8 (A) and Figure 8 (B) is the front view and side view of the second seal 14. Figure 8 (C) is Figure 8 H-H sectional view of the second seal 14 shown in (A).

[0040] Figure 9 (A) Figure 9 (C) represents the front view, side view, and rear view of the cover 15. Figure 9 (D) is Figure 9 (A) shows the I-I sectional view of cover 15.

[0041] Figure 10 (A) Figure 10 (D) is the front view, top view, bottom view, and side view of the axial force generating component 17. Figure 10 (E) is Figure 10 (C) shows an enlarged view of the J-J section of the axial force generating component 17. Figure 10 (F) is Figure 10 The enlarged view of the K-K section of the axial force generating component 17 shown in (D).

[0042] Figure 11 (A) is an enlarged view of an axial force generating member 17 mounted on a protrusion 18 of a partition 115 of a housing 11, viewed from the center of the rotary damper 1 according to an embodiment of the present invention. Figure 11 (B) is Figure 11 (A) shows an enlarged L-L cross-sectional view of the axial force generating component 17.

[0043] Figure 12 (A) and Figure 12 Figure (B) is an example of a braking system of a car in which a rotary damper 1 according to an embodiment of the present invention is applied.

[0044] Figure 13 (A) Figure 13 (B) is shown in Figure 12 The diagram shows an example of the operation of the braking system of the automobile when a malfunction occurs in the rotary damper 1.

[0045] Figure 14 This is a diagram used to illustrate the positional relationship between the rotary damper 1 and the plate 5 of the brake pedal 4. Detailed Implementation

[0046] Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

[0047] Figure 1 (A) Figure 1 (C) is a front view, a side view, and a rear view of the rotary damper 1 according to an embodiment of the present invention. Additionally, Figure 2 (A) is Figure 1 (A) shows the A-A sectional view of the rotary damper 1. Figure 2 (B) is Figure 1 The B-B cross-sectional view of the rotary damper 1 shown in (B) is also included. Figure 3 (A) and Figure 3 (B) is Figure 2 (A) shows an enlarged view of part A and part B of the rotary damper 1. Figure 4 (A) is Figure 2 (A) shows an enlarged view of part C of the rotary damper 1. Figure 4 (B) is Figure 2 (B) is an enlarged view of part D of the rotary damper 1.

[0048] As shown in the figure, the rotary damper 1 according to this embodiment includes: a housing 11; a rotor 12 rotatably housed within the housing 11 relative to the housing 11; a viscous fluid (not shown) such as oil or silicone filled within the housing 11; a cover 15 sealing the rotor 12 together with the viscous fluid within the housing 11; and a pair of axial force generating members 17. This rotary damper 1 is a damper for an automobile brake pedal. If the housing 11 rotates relative to the rotor 12 in the forward direction N, a strong damping torque is generated; conversely, if the housing 11 rotates relative to the rotor 12 in the reverse direction R, a weak damping torque is generated (see reference). Figure 1 (C) Figure 2 (B)

[0049] Figure 5 (A) is the front view of the outer casing 11. Figure 5 (B) is Figure 5 (A) shows a C-C sectional view of the outer casing 11. Figure 5 (C) is the rear view of the outer casing 11. Figure 5 (D) is Figure 5 (A) shows an enlarged view of part E of the outer casing 11. Figure 5 (E) is Figure 5 (A) shows an enlarged cross-sectional view of the outer casing 11 along line D-D. Figure 5 (F) is Figure 5 (A) shows an enlarged cross-sectional view of the outer shell 11 along the E-E line.

[0050] The outer casing 11 is formed of a thermoplastic resin such as polyacetal. As shown in the figure, a cylindrical chamber (a bottomed cylindrical space) 111 with one end open is formed inside the outer casing 11. An opening 113 for inserting the rotor 12 is formed at the bottom 112 of the cylindrical chamber 111. The rotor 12 is inserted through the lower end 123a of the rotor body 121 described later (see reference). Figure 6 The rotor 12 is inserted into the opening 113 and housed within the cylindrical chamber 111 such that the rotation axis 120 of the rotor 12 is aligned with the center line 110 of the cylindrical chamber 111 (see reference). Figure 2 (A)). Additionally, on the side wall 114 of the cylindrical chamber 111, a pair of partitions 115 are formed symmetrically with respect to the center line 110 of the cylindrical chamber 111. These partitions 115 protrude radially inward, with their end faces 116 approaching the outer peripheral surface 124 of the rotor body 121 (described later) of the rotor 12. Figure 6 ), dividing cylindrical chamber 111.

[0051] On a pair of partitions 115, a first seal 13 (described later) is installed respectively. Figure 4 (B)). Additionally, a pair of partitions 115 each have a portion formed on the back surface 153 of the cover 15 (see reference). Figure 9 On the upper surface 119 of the opposing surfaces, there is a protrusion 18 for mounting the axial force generating member 17. On the upper surface 180 of the protrusion 18, a groove 181 is formed along the radial direction of the cylindrical chamber 111 for inserting the adjustment part 174 of the axial force generating member 17 (described later). The bottom 182 of the groove is located on the side of the cover 15 closer to the upper surface 119 of the partition 115. In addition, on both sides 183 of the protrusion 18 along the radial direction of the outer casing 11, grooves 184 are formed along the center line 110 of the cylindrical chamber 111 for mounting the first pressing part 175 of the axial force generating member 17 (described later).

[0052] On the opening side 118 of the side wall 114 of the cylindrical chamber 111, a male threaded portion 152, which will be described later with respect to the cover 15, is formed (see reference). Figure 9 117. The female threaded part of the threaded engagement.

[0053] Additionally, on the outer peripheral surface 190 of the outer shell 11 on the opening side 118 of the cylindrical chamber 111, a pair of arms 19a and 19b of a clamping plate 5 are formed protruding radially outward. This plate 5 rotates around the pedal rotation center O in conjunction with the brake pedal 4 of the vehicle (see reference). Figure 12 ).

[0054] The arm 19a generates a strong damping torque in the outer shell 11 of the rotary damper 1 relative to the positive rotation direction N of the rotor 12 (see reference). Figure 2On (B)), located downstream of arm 19b. In addition, arm 19a has a curved portion 191 that bends in the rotational direction N, a support portion 192 and a connecting portion 193.

[0055] With respect to the curvature center C of the bend 191, the radial cross-section of the entire bend 191 has the same shape (see reference). Figure 5 (F)), and has a constant radial width W (refer to) Figure 5 (C)).

[0056] The support portion 192 is located at the end of the curved portion 191 and supports the plate 5, which rotates in conjunction with the brake pedal 4 around the pedal rotation center O in the forward rotation direction N (see reference). Figure 12 The plate 5 has a support surface 195 that contacts and supports the plate 5. Preferably, the angle α (refer to...) formed by the straight line passing through the support portion 192-side end 197 in the inner peripheral surface 196 of the bend 191 and the bend 191-side end 201 of the support surface 195 with the support surface 195 is... Figure 5 (C)) In the case where the bending part 191 is deformed by being pressed by the plate 5 (see reference). Figure 13 The angle α is the range within which the curved portion 191 of the support surface 195 can maintain line contact with the plate 5. However, if the angle α is less than 10 degrees, the arm portion 19a needs to be longer in order to reliably contact the support surface 195 with the plate 5, and the rotation damper 1 will become larger. Furthermore, if the angle α is greater than 90 degrees, the arm portion 19a will still become longer, and the rotation damper 1 will become larger. Typically, there is a limitation on the space for the rotation damper 1 to be installed on the brake pedal 4, and the increased size of the rotation damper 1 makes its installation on the brake pedal 4 difficult. The angle α is preferably between 30 and 60 degrees.

[0057] The connecting portion 193 extends radially outward from the outer peripheral surface 190 of the housing 11 and connects with the curved portion 191.

[0058] The arm 19b generates a strong damping torque in the outer shell 11 of the rotary damper 1 relative to the positive rotation direction N of the rotor 12 (see reference). Figure 2 On (B)), located upstream of arm 19a. Additionally, on arm 19b, a flat surface 194 is formed facing arm 19a and extending radially outward from the outer peripheral surface 190 of housing 11. The flat surface 194 supports a plate 5 that rotates in conjunction with brake pedal 4 around pedal rotation center O in the reverse direction R.

[0059] Figure 6 (A) and Figure 6 (B) is the front view and side view of rotor 12. Figure 6 (C) is Figure 6The rotor 12 shown in (A) is a cross-sectional view of F-F.

[0060] The rotor 12 is formed of a thermoplastic resin such as polyamide resin, and as shown in the figure, includes: a cylindrical rotor body 121; and a pair of blades (rotor vanes) 122 formed symmetrically with respect to the rotation axis 120 of the rotor 12. The blades 122 are formed along the rotation axis 120 of the rotor 12, protruding radially outward from the outer peripheral surface 124 of the rotor body 121, with their end faces 125 approaching the side wall surface 114 of the cylindrical chamber 111 of the outer casing 11, thus separating the cylindrical chamber 111. A flow path 126 is formed in the blade 122, extending along the rotation direction of the outer casing 11 and passing between the two side surfaces 127a and 127b of the blade 122. Furthermore, a second seal 14 (described later) is mounted on each of the pair of blades 122. Figure 4 (B)

[0061] In the rotor body 121, a double-sided flat through hole 128 is formed centered on the rotation axis 120 of the rotor 12 for inserting a double-sided flat shaft (not shown) that transmits rotational force from the outside to the rotor 12. Furthermore, the lower end portion 123a of the rotor body 121 is rotatably inserted into the opening 113 at the bottom 112 of the cylindrical chamber 111 formed in the outer casing 11 (see reference). Figure 4 (A)), the upper end portion 123b of the rotor body 121 is rotatably inserted into the opening 150 of the cover 15 (see later description). Figure 9 (refer to) Figure 3 (A) and (B)).

[0062] Alternatively, an O-ring 16a or other sealing element can be sandwiched between the lower end 123a of the rotor body 121 and the opening 113 of the cylindrical chamber 111 to prevent viscous fluid from leaking to the outside from the opening 113 of the cylindrical chamber 111 (see reference). Figure 4 (A)).

[0063] Figure 7 (A) and Figure 7 (B) is the front view and side view of the first seal 13. Figure 7 (C) is Figure 7 (A) is a G-G sectional view of the first seal 13.

[0064] As shown in the figure, the first seal 13 has a U-shape that can be installed on the partition 115 formed in the cylindrical chamber 111 of the housing 11. The bottom 130 is sandwiched between the end face 116 of the partition 115 and the outer peripheral surface 124 of the rotor body 121 of the rotor 12, thereby sealing their gap (see figure). Figure 4(B)). In addition, since the first seal 13 is disposed between the relatively rotating housing 11 and the rotor 12, its material is preferably a resin with excellent sliding properties such as polyamide.

[0065] Figure 8 (A) and Figure 8 (B) is the front view and side view of the second seal 14. Figure 8 (C) is Figure 8 H-H sectional view of the second seal 14 shown in (A).

[0066] As shown in the figure, the second seal 14 has a U-shape that can be mounted on the blade 122 of the rotor 12, including: having a width t1 greater than the direction of rotation of the blade 122 (see figure). Figure 6 (A)) The bottom 140 has a larger width t2; the end 141 integrally formed on one side of the bottom 140 has a width t3 greater than the radial width t3 of the flow path 126 formed on the blade 122 (see reference). Figure 6 The first foot 143 with a large width t4; and the second foot 144 integrally formed on the other side of the bottom 140 and having a width t5 smaller than the radial width t3 of the flow path 126 formed on the blade 122.

[0067] The second seal 14, installed on the blade 122, seals the gap between the blade 122 and the cylindrical chamber 111 of the housing 11 by clamping the bottom 140 between the end face 125 of the blade 122 and the side wall 114 of the housing 11 (see reference). Figure 4 (B)). Additionally, as... Figure 2 As shown in (B), if the outer casing 11 rotates relative to the rotor 12 in the forward rotation direction N, then the region 111a (see reference) is divided by the partition 115 and the blade 122 located downstream of the partition 115 in the forward rotation direction N. Figure 2 As the pressure of the viscous fluid inside (B) increases, the second seal 14 moves toward the N-direction of rotation, and the first foot 143 of the second seal 14 abuts against the side 127a of one side of the blade 122, blocking the flow path 126 formed in the blade 122.

[0068] On the other hand, if the outer casing 11 rotates relative to the rotor 12 in the reverse direction R, then the region 111b (see reference) is divided by the partition 115 and the blade 122 located downstream of the partition 115 in the reverse direction R. Figure 2As the pressure of the viscous fluid inside (B) increases, the second seal 14 moves in the reverse direction R, and the second foot 144 abuts against the other side 127b of the blade 122, opening the flow path 126 formed in the blade 122. Furthermore, since the second seal 14 is disposed between the relatively rotating housing 11 and the rotor 12, its material is preferably a resin with excellent sliding properties, such as polyamide.

[0069] Figure 9 (A) Figure 9 (C) represents the front view, side view, and rear view of the cover 15. Figure 9 (D) is Figure 9 (A) shows the I-I sectional view of cover 15.

[0070] As shown in the figure, on the cover 15, an opening 150 is formed facing the opening 113 of the bottom 112 of the cylindrical chamber 111 formed in the outer shell 11, for inserting the upper end 123b of the rotor body 121 of the rotor 12. Additionally, on the outer peripheral surface 151 of the cover 15, a male thread 152 is formed that engages with the female thread 117 of the opening side 118 formed on the side wall surface 114 of the cylindrical chamber 111. Furthermore, a gap G1 is formed between the lower surface (back side) 153 of the cover 15 and the upper surface 129 of the blades 122 of the rotor 12, functioning as a flow path for the viscous fluid filling the cylindrical chamber 111 (see reference). Figure 3 (B)). The gaps G1 that function as flow paths for viscous fluids can be adjusted by adjusting the amount of screwing of the cover 15 into the housing 11 (the amount of thread engagement between the male thread 152 of the cover 15 and the female thread 117 of the housing 11).

[0071] Alternatively, an O-ring 16b or similar sealing element can be sandwiched between the upper end 123b of the rotor body 121 of the rotor 12 and the opening 150 of the cover 15 to prevent viscous fluid from leaking to the outside from the opening 150 of the cover 15. Similarly, an O-ring 16c or similar sealing element can be sandwiched between the outer peripheral surface 151 of the cover 15 and the side wall surface 114 of the cylindrical chamber 111 to prevent viscous fluid from leaking to the outside from the threaded engagement portion of the male thread 152 of the cover 15 and the female thread 117 of the cylindrical chamber 111 of the outer casing 11 (see reference). Figure 3 (A) and Figure 3 (B)

[0072] Figure 10 (A) Figure 10 (D) is the front view, top view, bottom view, and side view of the axial force generating component 17. Figure 10 (E) is Figure 10 (C) shows an enlarged view of the J-J section of the axial force generating component 17. Figure 10(F) is Figure 10 The enlarged view of the K-K section of the axial force generating member 17 shown in (D) is also included. Figure 11 (A) is an enlarged view of the axial force generating member 17 mounted on the protrusion 18 of the partition 115 of the housing 11, viewed from the center of the rotary damper 1 according to this embodiment. Figure 5 (A) F direction is equivalent to the view. Figure 11 (B) is Figure 11 (A) shows an enlarged L-L cross-sectional view of the axial force generating component 17.

[0073] The axial force generating component 17 is formed from thermoplastic resin such as polyacetal, sintered metal or other plastically deformable components, or natural rubber, synthetic rubber or synthetic resin elastomer or other elastically deformable components. It is respectively installed on the protrusions 18 on the upper surfaces 119 of a pair of partitions 115 formed on the outer shell 11, sandwiched between the upper surface 119 of the partition 115 and the back surface 153 of the cover 15, sealing the gap between the back surface 153 of the cover 15 and the upper surface 119 of the partition 115, and generating axial force for the cover 15 to be screwed into the outer shell 11.

[0074] As shown, the axial force generating member 17 includes: a rectangular main body 170 having an upper surface 171 that contacts the back surface 153 of the cover 15; a pair of arms 173 formed on the lower surface 172 of the main body 170 and clamping the two sides 183 of the protrusion 18 formed on the upper surface 119 of the partition 115 of the outer casing 11 to hold the protrusion 18; and an adjustment portion 174 disposed between the pair of arms 173 and inserted into the groove 181 of the protrusion 18 protruding toward the protrusion 18.

[0075] Each pair of arms 173 has a first pressing portion 175 that presses against grooves 184 formed on the two sides 183 of the protrusion 18. The first pressing portions 175, together with the grooves 184 formed on the two sides 183 of the protrusion 18, serve a positioning function when the axial force generating member 17 is installed on the protrusion 18. Furthermore, through the first pressing portions 175, the pair of arms 173 forcefully hold the protrusion 18 so that the axial force generating member 17 does not detach from the protrusion 18. The pair of arms 173 have a length L2 greater than that of the adjusting portion 174 and a length L3 from the upper surface 119 of the separating portion 115 to the bottom 182 of the groove 181 of the protrusion 18 formed on the upper surface 119 (see reference). Figure 5 The total value of (E) is the shorter length L4 (< L2 + L3).

[0076] The adjusting part 174 has a depth L1 greater than that of the groove 181 of the protrusion 18 formed on the upper surface 119 of the partition part 115 (see reference). Figure 5The length L2 (>L1) of the adjustment portion 174 is greater than that of the base 177, and the width of its end portion 176 in the thickness direction is smaller than that of its base 177. Here, the groove 181 of the protrusion 18 has a size that allows for plastic or elastic deformation of the end portion 176 of the adjustment portion 174. In addition, the base 177 of the adjustment portion 174 has a second pressing portion 178 on both sides 179 in the thickness direction that presses against the side walls 185 of the groove 181 of the protrusion 18. Through the second pressing portion 178, the adjustment portion 174 is engaged with the groove 181 of the protrusion 18, and the axial force generating member 17 is more reliably prevented from falling off the protrusion 18.

[0077] Since the pair of arms 173 have a length L4 that is smaller than the sum of the length L2 of the adjustment portion 174 and the length L3 from the upper surface 119 of the partition portion 115 to the bottom 182 of the groove 181 of the protrusion 18, and the adjustment portion 174 has a length L2 that is larger than the depth L1 of the groove 181 of the protrusion 18, the end portion 176 of the adjustment portion 174 can abut against the bottom 182 of the groove 181 of the protrusion 18 without the pair of arms 173 abutting against the upper surface 119 of the partition portion 115. Furthermore, since the groove 181 of the protrusion 18 has a size that allows for plastic or elastic deformation of the end portion 176 of the adjustment portion 174, an axial force can be generated for the screwing of the cover 15 into the outer shell 11. In addition to the plastic or elastic deformation of the main body portion 170, the end portion 176 of the adjustment portion 174 also actively undergoes plastic or elastic deformation, thereby increasing the adjustment range of the gap G1 between the back surface 153 of the cover 15 and the upper surface 129 of the blade 122.

[0078] In the rotary damper 1 constructed as described above, if the outer casing 11 rotates relative to the rotor 12 in the forward rotation direction N (refer to...), Figure 2 (B) Then the second seal 14 moves toward the forward rotation direction N, and the first foot 143 of the second seal 14 abuts against the side surface 127a of one of the blades 122, blocking the flow path 126 formed on the blade 122. At this time, the gap between the end face 116 of the partition 115 and the outer peripheral surface 124 of the rotor body 121 of the rotor 12 is blocked by the first seal 13 installed on the partition 115 of the cylindrical chamber 111 of the housing 11, and the gap between the end face 125 of the blade 122 and the side wall surface 114 of the cylindrical chamber 111 of the housing 11 is blocked by the second seal 14 installed on the blade 122 of the rotor 12 (see reference). Figure 4 (B) Therefore, the movement of the viscous fluid filled in the cylindrical chamber 111 is restricted only through the gap G1 between the back surface 153 of the cover 15 and the upper surface 129 of the blade 122, and the region 111a (see reference) divided by the partition 115 and the blade 122 located downstream of the partition 115 in the forward rotation direction N. Figure 2The pressure of the viscous fluid within (B) increases. Consequently, a strong damping torque is generated.

[0079] Here, the gap G1 between the back surface 153 of the cover 15 and the upper surface 129 of the blade 122 can be adjusted by adjusting the amount of screwing of the cover 15 into the housing 11 (the amount of thread engagement between the male thread portion 152 of the cover 15 and the female thread portion 117 of the housing 11). Therefore, by adjusting the amount of movement of the viscous fluid moving through this gap G1, the damping torque generated by rotation can be adjusted.

[0080] Furthermore, by arranging an axial force generating member 17 that applies a reaction force to the cover 15 between the back surface 153 of the cover 15 and the upper surface 119 of the partition 115, an axial force can be generated for the cover 15 as it is screwed into the outer shell 11, preventing viscous fluid from leaking from the threaded engagement portion of the male threaded portion 152 of the cover 15 and the female threaded portion 117 of the outer shell 11, and increasing the adjustment margin of the clearance G1, the adjustment range of the damping torque can be expanded.

[0081] On the other hand, if the outer casing 11 rotates relative to the rotor 12 in the opposite direction R (refer to...) Figure 2 (B) Then the second seal 14 moves toward the reverse direction R side, and the second foot 144 abuts against the other side 127b of the blade 122, opening the flow path 126 formed in the blade 122. Therefore, the movement of the viscous fluid filled in the cylindrical chamber 111 is carried out not only through the gap G1 between the back surface 153 of the cover 15 and the upper surface 129 of the blade 122, but also through the flow path 126 formed in the blade 122. Thus, the area 111b (refer to) divided by the partition 115 and the blade 122 located on the reverse direction R side opposite to the partition 115 is opened. Figure 2 The pressure of the viscous fluid within (B) did not increase. Consequently, a weak damping torque was generated.

[0082] Figure 12 (A) and Figure 12 (B) is a diagram showing an example of a braking system of a car in which the rotary damper 1 of this embodiment is applied.

[0083] The braking system includes: a shaft 2 disposed at the pedal rotation center O; a brake arm 3 rotatably mounted on the shaft 2 and connected to the brake master cylinder 6; a brake pedal 4 mounted at the end of the brake arm 3; a plate 5 mounted on the brake arm 3 in a manner that rotates around the pedal rotation center O in conjunction with the brake pedal 4; and a rotation damper 1 mounted on the shaft 2 in a manner that is clamped into the plate 5 by a pair of arms 19a, 19b.

[0084] Here, the end of shaft 2 is cut flat on both sides, and this end is inserted into the through hole 128 of rotor 12 of rotary damper 1, which is also cut flat on both sides. Rotor 12 is fixed to shaft 2, and its rotation around the pedal rotation center O is constrained. Furthermore, rotary damper 1 is installed such that when brake pedal 4 is depressed and plate 5 rotates around pedal rotation center O in the forward direction N, plate 5 is supported by the support surface 195 of support portion 192 of arm 19a; when brake pedal 4 is released and plate 5 rotates around pedal rotation center O in the reverse direction R, plate 5 is supported by the flat surface 194 of arm 19b. Additionally, plate 5 has a base portion 199 (see reference) that is not between the pair of arms 19a, 19b. Figure 12 The (A) is sandwiched between the support surface 195 of the support portion 192 of the arm 19a and the flat surface 194 of the arm 19b in a manner that causes interference, and is held by a pair of arms 19a and 19b.

[0085] In the braking system described above, such as Figure 12 As shown in (A), when the brake pedal 4 is pressed, the master cylinder 6 is compressed, and the plate 5 rotates in the forward direction N around the pedal rotation center O. This rotational torque is transmitted to the housing 11 of the rotary damper 1 via the arm 19a. Here, since the rotation of the rotor 12 of the rotary damper 1 around the pedal rotation center O is constrained, the housing 11 rotates relative to the rotor 12 in the forward direction N, generating a strong damping torque. As a result, a strong reaction force can be applied to the pressing of the brake pedal 4, providing a good braking feel.

[0086] However, in Figure 12 In (A), the stress generated in the arm 19a due to the rotational torque in the forward direction N transmitted from the plate 5 to the arm 19a is concentrated at the bend 191 of the arm 19a. Therefore, even if the rotational damper 1 malfunctions and the rotation of the housing 11 relative to the rotor 12 in the forward direction N is obstructed, such as Figure 13 As shown in (A) to (C), by forcefully pressing the brake pedal 4, the bent portion 191 can be deformed, and sometimes broken, releasing the plate 5 from the support of the arm 19a, thus compressing the master cylinder 6 to apply braking. At this time, because the bent portion 191 is connected to the space D (see reference) between the bent portion 191 and the housing 11 via the connecting portion 193, Figure 13 The deformation of (A) allows the bent portion 191 to deform without interfering with the brake pedal 4. Furthermore, the bent portion 191 will not obstruct the movement of the brake pedal 4 even after it breaks.

[0087] In addition, such as Figure 12As shown in (B), when the brake pedal 4 is released from its depressed position, the master cylinder 6 extends, and the plate 5 rotates in the reverse direction R around the pedal rotation center O. This rotational torque is transmitted to the housing 11 of the rotary damper 1 via the arm 19b. Here, since the rotation of the rotor 12 of the rotary damper 1 around the pedal rotation center O is constrained, the housing 11 rotates relative to the rotor 12 in the reverse direction R. The damping torque generated in this case is a weak damping torque. Therefore, the extension force of the master cylinder 6 overcomes this weak damping torque, and the brake pedal 4 returns to its initial position before being depressed.

[0088] In addition, such as Figure 14 As shown, the distance from the center (pedal rotation center) O of the rotary damper 1 to the plate 5 is defined as r1, the distance from the center O of the rotary damper 1 to the outer peripheral surface 198 of the support portion 192 side end 197 of the curved portion 191 is defined as r2, and the distance from the center O of the rotary damper 1 to the outermost peripheral portion (outermost peripheral portion of the connecting portion 193) 200 of the base portion 199 between the pair of arms 19a and 19b is defined as r3. In this case, it is preferable that r1 > r2 and r1 > r3. When r1 ≤ r2, the arm 19a becomes longer and the rotary damper 1 becomes larger. Generally, there is a limitation in the installation space of the rotary damper 1 toward the brake pedal 4, and the large size of the rotary damper 1 makes its installation toward the brake pedal 4 difficult. In addition, when r1≤r3, the plate 5 contacts not only the support surface 195 but also the base portion 199. When the arm portion 19a is pressed by the plate 5, it is difficult to concentrate the stress generated in the arm portion 19a through this force on the bending portion 191.

[0089] The above describes one embodiment of the present invention.

[0090] In this embodiment, by setting the rotation damper 1 so that the plate 5 presses the arm 19a located on the downstream side in the forward rotation direction N in conjunction with the pressing of the brake pedal 4, a strong damping torque can be generated for the pressing of the brake pedal 4.

[0091] Furthermore, the outer shell 11 is formed of thermoplastic resin, and a bend 191 is provided on the arm 19a, one of the pair of arms 19a and 19b, located downstream in the forward rotation direction N. A support 192 located at the end of the arm 19a, beyond the bend 191, supports the plate 5 rotating in the forward rotation direction N. Therefore, the stress generated in the arm 19a due to the rotational torque in the forward rotation direction N transmitted from the plate 5 to the arm 19a is concentrated in the bend 191. Thus, even if the rotational damper 1 malfunctions and the rotation of the outer shell 11 relative to the rotor 12 in the forward rotation direction N is obstructed, the bend 191 can be broken by forcefully pressing the brake pedal 4, releasing the plate 5 from the support of the arm 19a, and compressing the master cylinder 6 to apply braking.

[0092] Furthermore, the radial cross-section of the curved portion 191 is of the same shape throughout the entire curved portion 191 relative to its curvature center C (see reference). Figure 5 (F)), and the radial width W is constant (refer to...) Figure 5 Therefore, the deviation of the brake pedal depressing force required to reduce the damage to the bent portion 191 caused by the deviation of the pressing direction of the plate 5 applied to the support portion 192 can be reduced.

[0093] Therefore, according to this embodiment, a rotary damper 1 can be provided that is suitable as a brake pedal damper with fail-safe function.

[0094] Furthermore, in this embodiment, the arm 19a has a connecting portion 193 that extends radially outward from the outer peripheral surface 190 of the housing 11 and connects to the bent portion 191. This connecting portion 193 ensures space for the bent portion 191 to flex in the forward rotation direction N. Therefore, even if the rotational damper 1 malfunctions, causing the rotation of the housing 11 relative to the rotor 12 in the forward rotation direction N to be obstructed, by forcefully pressing the brake pedal 4, the bent portion 191 flexes in the forward rotation direction N, and the brake pedal 4 moves in the forward rotation direction N, resulting in a braking feel with minimal disharmony.

[0095] Furthermore, according to this embodiment, in the rotational damper 1 that generates damping torque against the applied rotational force by restricting the movement of the filled viscous fluid, the cover 15 is configured to screw into the outer casing 11, and the gap G1 between the back surface 153 of the cover 15 and the upper surface 129 of the blade 122 can be adjusted by the amount of screwing the cover 15 into the outer casing 11. Therefore, without increasing the number of parts, the amount of movement of the viscous fluid moving through the gap G1 can be adjusted through a simple configuration and simple operation, thereby adjusting the damping torque generated by rotation.

[0096] Furthermore, according to this embodiment, by distributing an axial force generating member 17, which is formed of a plastically deformable or elastically deformable member and imparts a reaction force to the cover 15, between the back surface 153 of the cover 15 and the upper surface 119 of the partition 115, an axial force is generated for the screwing of the cover 15 into the outer shell 11. This prevents viscous fluid from leaking from the threaded engagement portion of the male threaded portion 152 of the cover 15 and the female threaded portion 117 of the outer shell 11, and increases the adjustment margin of the gap G1, thereby expanding the adjustment range of the damping torque.

[0097] Furthermore, in this embodiment, a protrusion 18 is provided on the upper surface 119 of the partition 115, and a pair of arms 173 are provided on the axial force generating member 17 to clamp and hold the protrusion 18. Therefore, the axial force generating member 17 can be easily installed on the partition 115.

[0098] Furthermore, in this embodiment, an adjustment portion 174 is provided in the axial force generating member 17. This adjustment portion 174 is disposed between a pair of arms 173, protruding toward a protrusion 18 provided on the upper surface 119 of the partition portion 115, and inserting into the groove 181 of the protrusion 18 to abut against the bottom 182 of the groove 181. The groove 181 of the protrusion 18 is set to allow for plastic or elastic deformation of the end portion 176 of the adjustment portion 174. Therefore, as the cover 15 is screwed into the outer casing 11, the end portion 176 of the adjustment portion 174 presses against the bottom 182 of the groove 181, actively generating plastic or elastic deformation, thereby further increasing the adjustment range of the gap G1.

[0099] Furthermore, in this embodiment, each pair of arms 173 of the axial force generating member 17 has a first pressing portion 175 that presses against grooves 184 formed on both sides 183 of the protrusion 18 (formed on the upper surface 119 of the partition 115). Through these first pressing portions 175, the pair of arms 173 can forcefully hold the protrusion 18 in a manner that prevents the axial force generating member 17 from falling off. In addition, the first pressing portions 175, together with the grooves 184 formed on both sides 183 of the protrusion 18, serve a positioning function when the axial force generating member 17 is installed on the protrusion 18, enabling the axial force generating member 17 to be accurately installed on the protrusion 18.

[0100] Furthermore, in this embodiment, the adjustment portion 174 of the axial force generating member 17 has a second pressing portion 178 on both sides 179 of the base 177 that presses against the two side walls 185 of the groove 181 of the protrusion 18. Through this second pressing portion 178, the adjustment portion 174 is fitted into the groove 181 of the protrusion 18, which can more reliably prevent the axial force generating member 17 from falling off the protrusion 18.

[0101] Furthermore, according to this embodiment, by using a resin with excellent sliding properties such as polyamide in the first seal 13 and the second seal 14, the first seal 13 and the second seal 14 function as sliding bearings on the outer peripheral surface 124 of the rotor body 121 that slidably supports the rotor 12. Therefore, they can absorb the shaking caused by the eccentricity of the shaft 2 that transmits rotational force from the outside to the rotor 12, and enable the shaft 2 to rotate smoothly.

[0102] Furthermore, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of its key points.

[0103] For example, in the above embodiment, as a flow path for viscous fluid other than the flow path 126 formed on the blade 122, the gap G1 between the back surface 153 of the cover 15 and the upper surface 129 of the blade 122 is used as an example. However, the present invention is not limited to this. It is also possible to configure the axial force generating member 17 so as not to block the gap between the back surface 153 of the cover 15 and the upper surface 119 of the partition 115, so as a flow path for viscous fluid other than the flow path 126 formed on the blade 122, and use the gap between the back surface 153 of the cover 15 and the upper surface 129 of the partition 115 in addition to using the gap G1 between the back surface 153 of the cover 15 and the upper surface 129 of the blade 122.

[0104] In this embodiment, an example is given where a pair of partitions 115 are provided in the cylindrical chamber 111 and a pair of blades 122 are provided in the rotor 12. However, the present invention is not limited thereto. If the number of partitions 115 formed in the cylindrical chamber 111 and the number of blades 122 formed in the rotor 12 are the same, then one or more may be formed.

[0105] In this embodiment, the second seal 14 installed on the blade 122 functions as a check valve to open and close the flow path 126 formed on the blade 122, but the present invention is not limited thereto. Alternatively, the check valve may be provided separately from the second seal 14. If the housing 11 rotates relative to the rotor 12 in the forward direction N, the check valve will block the flow path 126 formed on the blade 122; if the housing 11 rotates relative to the rotor 12 in the reverse direction R, the check valve will open the flow path 126 formed on the blade 122.

[0106] In this embodiment, a flow path 126 is formed in the blade 122, extending through both sides 127a and 127b of the blade 122 along the rotation direction of the outer casing 11. However, the present invention is not limited to this. Alternatively, or together with the blade 122, a flow path extending through both sides of the partition 115 along the rotation direction of the outer casing 11 may be formed in the partition 115. In this case, a check valve is provided. If the outer casing 11 rotates relative to the rotor 12 in the forward direction N, the check valve will block the flow path formed in the partition 115. If the outer casing 11 rotates relative to the rotor 12 in the reverse direction R, the check valve will open the flow path formed in the partition 115.

[0107] Alternatively, when the partition 115 forms a flow path, the first seal 13 may be formed in the same shape as the second seal 14, that is, in a shape including the following parts: a bottom having a width greater than the circumferential width of the inner periphery of the partition 115; a first foot integrally formed at one end of the bottom and having a width greater than the radial width of the flow path formed in the partition 115; and a second foot integrally formed at the other end of the bottom and having a width smaller than the radial width of the flow path formed in the partition 115. Furthermore, the first seal 13 can also function as a check valve as follows: if the housing 11 rotates relative to the rotor 12 in the forward direction N, the first foot of the first seal 13 abuts against one side of the partition 115, blocking the flow path formed in the partition 115; if the housing 11 rotates relative to the rotor 12 in the reverse direction R, the first foot of the first seal 13 moves away from one side of the partition 115, and the second foot abuts against the other side of the partition 115, opening the flow path formed in the partition 115.

[0108] In addition, if no flow path 126 is formed in the blade 122, the second seal 14 can be of any shape if it can seal the gap between the end face 125 of the blade 122 and the side wall face 114 of the cylindrical chamber 111 of the housing 11.

[0109] In this embodiment, a first seal 13 is installed in the partition 115 of the cylindrical chamber 111 of the outer casing 11, but the present invention is not limited thereto. The first seal 13 may also be omitted. Similarly, a second seal 14 is installed in the blades 122 of the rotor 12, but the second seal 14 may also be omitted.

[0110] In this embodiment, an axial force generating member 17, formed of a plastically deformable or elastically deformable component, is disposed between the back surface 153 of the cover 15 and the upper surface 119 of the partition 115 to generate axial force for screwing the cover 15 into the outer shell 11. However, the present invention is not limited to this. The outer shell 11 may also be formed of thermoplastic resin, and a protrusion that abuts against the back surface 153 of the cover 15 may be integrally formed on the upper surface 119 of the partition 115 as the axial force generating part. In this case, the axial force generating part (protrusion) generates axial force for screwing the cover 15 into the outer shell 11, which can prevent viscous fluid from leaking from the threaded engagement portion of the male threaded portion 152 of the cover 15 and the female threaded portion 117 of the outer shell 11, and through plastic deformation, the adjustment range of the gap G1 can be increased, and the adjustment range of the damping torque can be expanded.

[0111] Explanation of reference numerals in the attached figures

[0112] 1: Rotary damper, 2: Shaft, 3: Brake arm

[0113] 4: Brake pedal, 5: Brake plate, 6: Master cylinder

[0114] 11: Casing; 12: Rotor; 13: First seal.

[0115] 14: Second seal; 15: Cover; 16a, 16b, 16c: O-rings;

[0116] 17: Axial force generating component; 18: Protrusion; 111: Cylindrical chamber.

[0117] 19a, 19b: Arm section; 112: Bottom of cylindrical chamber 111.

[0118] 113: Opening of cylindrical chamber 111; 114: Side wall of cylindrical chamber 111.

[0119] 115: Divider; 116: End face of divider 115

[0120] 117: Female threaded portion; 118: Opening side of cylindrical chamber 111;

[0121] 119: Upper surface of partition 115; 121: Rotor body;

[0122] 122: Blade; 123a, 123b: Ends of rotor body 121;

[0123] 124: Outer circumferential surface of the rotor body; 125: End face of blade 122.

[0124] 126: Flow path; 127a, 127b: Side surfaces of blade 122.

[0125] 128: Through hole in rotor body 121; 129: Upper surface of blade 122;

[0126] 130: Bottom of the first seal 13, 140: Bottom of the second seal 14,

[0127] 141, 142: The ends of the bottom 140 of the second seal 14,

[0128] 143: The first foot of the second seal 14,

[0129] 144: The second foot of the second seal 14,

[0130] 150: Opening of lid 15; 151: Outer circumference of lid 15.

[0131] 152: Male threaded portion; 153: Lower surface of cap 15.

[0132] 170: Main body of axial force generating component 17; 171: Upper surface of main body 170.

[0133] 172: Lower surface of main body 170; 173: Arm portion;

[0134] 174: Adjustment section; 175: First crimping section;

[0135] 176: The end portion of the adjusting part 174; 177: The base of the adjusting part 174.

[0136] 178: Second crimped part; 179: Side of base 177;

[0137] 180: Upper surface of protrusion 18; 181: Groove; 182: Groove bottom.

[0138] 183: Side of protrusion 18; 184: Groove; 185: Side wall of groove 181.

[0139] 190: Outer peripheral surface of outer casing 11; 191: Bent portion; 192: Support portion.

[0140] 193: Connecting part, 194: Flat surface, 195: Supporting surface

[0141] 196: Inner circumferential surface of the curved portion 191,

[0142] 197: The end portion of the support portion 192 of the curved portion 191,

[0143] 198: Outer peripheral surface of the curved portion 191

[0144] 199: The base portion between arm 19a and 19b.

[0145] 200: The outermost periphery of the base portion 199,

[0146] 201: The curved portion 191 of the support surface 195.

Claims

1. A rotary damper for an automobile brake pedal, the rotary damper comprising a rotor and a housing rotatably housing the rotor, wherein a damping torque is generated when the housing rotates relative to the rotor in the forward direction, characterized in that... The aforementioned housing is formed of thermoplastic resin and has a pair of arms protruding radially outward, which clamp a plate that rotates around the pedal's rotation center in conjunction with the brake pedal. The arm located downstream of the aforementioned pair of arms in the forward rotation direction has: A curved section with a constant width; and A support portion is located at a position closer to the end of the aforementioned curved portion and supports the aforementioned plate.

2. The rotary damper as described in claim 1, characterized in that, The arm located on the downstream side of the aforementioned forward rotation direction also has a connecting portion that extends radially outward from the aforementioned outer casing and connects to the aforementioned curved portion.

3. The rotary damper as described in claim 1, characterized in that, The aforementioned housing has: A cylindrical chamber filled with a viscous fluid; and A partition portion protrudes radially inward from the side wall of the cylindrical chamber and divides the cylindrical chamber. The rotor described above has: A cylindrical rotor body, the outer peripheral surface of which is close to the end face of the aforementioned partition; and The blade protrudes radially outward from the outer peripheral surface of the rotor body and divides the cylindrical chamber; the end face of the blade is close to the side wall surface of the cylindrical chamber. The aforementioned rotary damper also features: A flow path, formed in the aforementioned partition or blade, extending through the space between the two sides of the aforementioned partition or blade along the rotational direction of the aforementioned housing; and A check valve that blocks the flow path when the housing rotates relative to the rotor in the forward direction and releases the flow path when the housing rotates relative to the rotor in the reverse direction.

4. The rotary damper as described in claim 2, characterized in that, The aforementioned housing has: A cylindrical chamber filled with a viscous fluid; and A partition portion protrudes radially inward from the side wall of the cylindrical chamber and divides the cylindrical chamber. The rotor described above has: A cylindrical rotor body, the outer peripheral surface of which is close to the end face of the aforementioned partition; and The blade protrudes radially outward from the outer peripheral surface of the rotor body and divides the cylindrical chamber; the end face of the blade is close to the side wall surface of the cylindrical chamber. The aforementioned rotary damper also features: A flow path, formed in the aforementioned partition or blade, extending through the space between the two sides of the aforementioned partition or blade along the rotational direction of the aforementioned housing; and A check valve that blocks the flow path when the housing rotates relative to the rotor in the forward direction and releases the flow path when the housing rotates relative to the rotor in the reverse direction.

5. The rotary damper as described in claim 3, characterized in that, The aforementioned rotary damper further comprises at least one of a first sealing member that seals the gap between the end face of the aforementioned partition and the outer peripheral surface of the aforementioned rotor body, and a second sealing member that seals the gap between the end face of the aforementioned blade and the side wall surface of the aforementioned cylindrical chamber.

6. The rotary damper as described in claim 4, characterized in that, The aforementioned rotary damper further comprises at least one of a first sealing member that seals the gap between the end face of the aforementioned partition and the outer peripheral surface of the aforementioned rotor body, and a second sealing member that seals the gap between the end face of the aforementioned blade and the side wall surface of the aforementioned cylindrical chamber.

7. A braking system comprising the rotational damper according to any one of claims 1 to 6, characterized in that, The above-mentioned braking system includes: A shaft is positioned at the center of rotation of the pedal; A brake arm, which is rotatably mounted on the aforementioned shaft and connected to the master cylinder; A brake pedal, which is mounted at the end of the aforementioned brake arm; as well as A plate, which is mounted on the brake arm in a manner that rotates around the pedal's rotation center in conjunction with the brake pedal. The aforementioned rotary damper fixes the rotor to the aforementioned shaft and constrains the rotation of the rotor about the rotation center of the aforementioned pedal. The aforementioned rotary damper is installed as follows: when the brake pedal is depressed and the plate rotates about the pedal's rotation center in the forward direction, the plate is supported by the support portion of the arm located downstream in the forward direction of rotation; when the brake pedal is released and the plate rotates about the pedal's rotation center in the reverse direction, the plate is supported by the arm located upstream in the forward direction of rotation. The plate is clamped and held by the pair of arms in a manner that does not interfere with the base portion between the pair of arms.

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